阅读说明：本技术 活塞压缩机阀和活塞压缩机阀操作方法 (Piston compressor valve and method for operating a piston compressor valve ) 是由 A·博塞尔 于 2018-03-27 设计创作，主要内容包括：本发明涉及活塞压缩机阀(1),包括具有多个通道开口(2a)的阀座(2)、能绕旋转轴线(D)旋转用于启闭该通道开口(2a)的闭合件(3)以及用于旋转该闭合件(3)的调节驱动机构(5),其中该阀座(2)具有所述通道开口(2a)通入其中的端侧(2b),其中该闭合件(3)在旋转轴线(D)的延伸方向上移动地连接至调节驱动机构(5),使得闭合件(3)既能绕旋转轴线(D)旋转且也能在旋转轴线(D)的延伸方向上相对于端侧(2b)移动,还包括用于检查活塞压缩机阀(1)的状态变量(E)的传感器(8)和根据状态变量(E)启动该调节驱动机构(5)的控制装置(20)。(The invention relates to a piston compressor valve (1) comprising a valve seat (2) having a plurality of passage openings (2a), a closure element (3) which can be rotated about a rotational axis (D) for opening and closing the passage openings (2a), and an actuating drive (5) for rotating the closure element (3), wherein the valve seat (2) has an end face (2b) into which the passage opening (2a) opens, wherein the closure element (3) is connected to an adjustment drive (5) in a manner such that it can be displaced in the direction of extension of the axis of rotation (D), the closing element (3) can be rotated about a rotational axis (D) and can also be displaced in the direction of extension of the rotational axis (D) relative to the end face (2b), and a sensor (8) for detecting a state variable (E) of the piston compressor valve (1) and a control device (20) for actuating the actuating drive (5) as a function of the state variable (E).)

1. Piston compressor valve (1) comprising a valve seat (2) having a plurality of passage openings (2a), a closure member (3) which is rotatable about a rotational axis (D) for opening and closing the passage openings (2a), and an adjustment drive (5) for rotating the closure member (3), wherein the valve seat (2) has an end side (2b) into which the passage openings (2a) open, wherein the closure member (3) is designed in one piece, wherein the closure member (3) is fixedly connected to the rotational axis (D), wherein the closure member (3) is connected to the adjustment drive (5) so as to be automatically movable in the direction of extension of the rotational axis (D) such that the closure member (3) is rotatable about the rotational axis (D) by the adjustment drive (5) and automatically displaceable relative to the end side (2b) in the direction of extension of the rotational axis (D), and further comprising a sensor (8) for detecting a state variable (E) of the piston compressor valve (1) and a control device (20) for actuating the actuating drive (5) as a function of the state variable (E).

2. Valve according to claim 1, characterized in that the sensor (8) is designed to detect a state variable (E) of the closing member (3) except for the angle of rotation of the closing member (3).

3. A valve according to claim 1 or 2, wherein the closing member (3) is coupled to the adjustment drive (5) by a coupling (9) springing in the direction of extension of the axis of rotation (D).

4. A valve according to claim 3, wherein the coupling (9) is rotationally stable with respect to rotation about the axis of rotation (D).

5. Valve according to one of the preceding claims, characterized in that the closure member (3) is coupled to the adjustment drive (5) by means of a shaft (4), and that the shaft (4) is mounted so as to be movable not only in the direction of extension of the axis of rotation (D) but also in the direction of rotation of the axis of rotation (D).

6. Valve according to one of the preceding claims, characterized in that the sensor (8) is designed to detect a movement of the closure member (3) or the shaft (4) in the direction of extension of the axis of rotation (D) as the state variable (E).

7. A valve according to one of claims 1 to 5, characterized in that the sensor (8) is designed to detect direct contact between the closure member (3) and the valve seat (2) as the state variable (E).

8. A valve according to one of claims 1 to 5, characterized in that the sensor (8) is designed to detect a pressure difference over the closing member (3) as the state variable (E).

9. Valve according to one of claims 5 to 8, characterized in that the valve seat (2) comprises a central bore (2e), the passage opening (2a) extending in the radial direction of the central bore (2e), the central bore (2e) being designed both as a radial bearing and as an axial bearing, in that the shaft (4) is mounted rotatably and displaceably in the direction of extension of the axis of rotation (D), in that the closure member (3) is fixedly connected to the shaft (4), and in that the shaft (4) is connected to the adjustment drive (5) by means of the coupling (9).

10. Valve according to one of claims 3 to 9, characterized in that the closure member (3) is arranged between the valve seat (2) and the elastic coupling (9) in order to form a pressure valve, or that the valve seat (2) is arranged between the closure member (3) and the elastic coupling (9) in order to form a suction valve.

11. A valve according to any one of the preceding claims, characterized in that the valve seat (2) has a passage opening (2a) extending in the radial direction of the axis of rotation (D), which passage opening has a width of at most 10 ° in the circumferential direction of the axis of rotation (D), so that the closure member (3) can be switched back and forth between an open position and a closed position by rotating at most 10 ° about the axis of rotation (D).

12. A valve according to any of the preceding claims, characterized in that the torsion spring (7) comprises an inner torsion spring (7a) and an outer torsion spring (7b) which are arranged coaxially with the rotation axis (D) and extend in the direction of extension of the rotation axis (D), the inner torsion spring (7a) being connected at its first end to the adjustment drive (5), the outer torsion spring (7b) being connected at its first end to a cover (6b), the inner and outer torsion springs (7a,7b) being connected at their second ends to each other, and the torsion spring (7) being connected at its second end to the coupling (9) or the shaft (4).

13. A piston compressor valve (1) control method, wherein the piston compressor valve (1) comprises a valve seat (2) with a plurality of passage openings (2a), a closure member (3) rotatable about a rotational axis (D) for opening and closing the passage openings (2a), and an adjustment drive (5) for rotating the closure member (3), wherein the closure member (3) is designed to be integral and fixedly connected to the rotational axis (D), wherein the rotational axis (D) is mounted so as to be displaceable in the direction of extension of the rotational axis (D), wherein the closure member (3) is automatically displaced in the direction of extension of the rotational axis (D) and abuts against the valve seat (2) or lifts off the valve seat (2) depending on a working gas pressure acting on the valve (1), wherein a state variable (E) of the piston compressor valve (1) is measured, and wherein the closure member (3) is rotated about the axis of rotation (D) by the adjustment drive (5) in dependence on the state variable (E).

14. Method according to claim 13, characterized in that the lift of the closing element (3) in the direction of extension of the axis of rotation (D) is measured as the state variable (E) and that the closing element (3) is rotated from a closed position to an open position when the lift is measured.

15. Method according to claim 14, characterised in that once said lifting exceeds a predetermined minimum distance (D)_min) The closure member (3) is rotated from the closed position to the open position.

16. A method according to claim 15, characterised in that the distance between the sealing surface (3d) of the closure member (3) and the end side (2b) of the valve seat (2) is measured as the state variable (E) and if the distance exceeds a maximum of 0.1mmSmall distance (D)_min) The closure member (3) is rotated from the closed position to the open position.

17. Method according to claim 13, characterized in that the differential pressure on the valve seat (2) is measured as the state variable (E) and if the differential pressure is below a predetermined minimum pressure (P)_min) The closure member (3) is rotated from the closed position to the open position.

Technical Field

The present invention relates to a piston compressor valve according to the preamble of claim 1. The invention also relates to a piston compressor valve operating method according to the preamble of claim 13.

Background

Document WO01/59266a1 discloses a valve for a piston compressor. The valve comprises a valve seat and a rotatable closure member, wherein the closure member opens and closes a passage opening provided in the valve seat depending on its rotational position. Such known valves have the disadvantage that relatively severe wear occurs, the opening and closing of the valve is relatively long lasting and the valve sealing function is reduced over time due to the wear that occurs.

Document WO2009/050215a2 discloses another valve for a piston compressor. This valve also has the disadvantage of wear and the long duration of opening and closing of the valve.

Disclosure of Invention

It is an object of the present invention to create a more advantageous piston compressor valve comprising a rotatable closure member.

This object is achieved by a piston compressor valve comprising the features of claim 1. The dependent claims 2 to 12 relate to further advantageous designs. The object is also achieved by a piston compressor valve control method comprising the features of claim 13. Dependent claims 14-17 relate to further advantageous method steps.

This object is achieved in particular by a piston compressor valve comprising a valve seat with a plurality of passage openings, a closure element which is rotatable about an axis of rotation for opening and closing the passage openings, and an actuating drive for rotating the closure element, wherein the valve seat has an end face into which the passage openings open, wherein the closure element is connected to the actuating drive so as to be movable in the direction of extension of the axis of rotation, such that the closure element is rotatable about the axis of rotation and can be displaced relative to the end face in the direction of extension of the axis of rotation, and comprising a sensor for detecting a state variable of the piston compressor valve and a control device for actuating the actuating drive as a function of the state variable.

The object is also achieved in particular by a piston compressor valve comprising a valve seat with a plurality of passage openings, a closure element which can be rotated about an axis of rotation for opening and closing the passage openings, an actuating drive for rotating the closure element, wherein the valve seat has an end side into which the passage openings open, wherein the closure element is designed in one piece or in one piece, wherein the closure element is fixedly connected to the axis of rotation, wherein the closure element is connected to the actuating drive so as to be automatically displaceable in the direction of extension of the axis of rotation both about the axis of rotation and relative to the end side by means of the actuating drive, and comprising a sensor for detecting a state variable of the piston compressor valve and a control device for actuating the actuating drive as a function of the state variable.

The object is also achieved in particular by a piston compressor valve control method, wherein the piston compressor valve comprises a valve seat with at least one passage opening, a closure member which is rotatable about an axis of rotation for opening and closing the passage opening, and an adjustment drive for rotating the closure member, wherein the closure member is mounted so as to be displaceable in the direction of extension of the axis of rotation, wherein the closure member bears against or lifts off the valve seat as a function of a working gas pressure acting on the valve, wherein a state variable of the piston compressor valve is measured, and wherein the closure member is rotated about the axis of rotation as a function of the state variable.

The object is also achieved in particular by a piston compressor valve control method, wherein the piston compressor valve comprises a valve seat with a plurality of passage openings, a closure member which can be rotated about an axis of rotation for opening and closing the passage openings, and an adjustment drive for rotating the closure member, wherein the closure member is designed as one piece or one piece and is fixedly connected to the axis of rotation, wherein the axis of rotation and thus the closure member can be displaced in the direction of extension of the axis of rotation, wherein the closure member is automatically displaced in the direction of extension of the axis of rotation and bears against or lifts off the valve seat as a function of a working gas pressure acting on the valve, wherein a state variable of the piston compressor valve is measured, and wherein the closure member is rotated about the axis of rotation by the adjustment drive as a function of the state variable.

The piston compressor valve according to the invention has the advantage that its closure element is lifted automatically off the valve seat in the event of a corresponding pressure difference, so that the closure element is advantageously actuated only when it is lifted off the valve seat or is rotated by means of an active actuating mechanism in order to completely open the passage opening. The closing element is thus not subjected to friction or only to a small amount of friction during opening, which on the one hand results in slight wear of the closing element and the valve seat and on the other hand allows the closing element to be rotated particularly quickly with a low force, thereby fully opening the piston compressor valve. Furthermore, the piston compressor valve is advantageously completely closed, so that the closure member is rotated in the lifted state relative to the valve seat from an open position into a closed position, in which the passage opening, viewed in the direction of extension of the axis of rotation, is completely covered by the closure member, and the closure member is subsequently or simultaneously or in a staggered manner automatically displaced by the existing pressure difference toward the valve seat until the closure member abuts against the valve seat and completely covers the passage opening, so that the piston compressor valve is completely closed again, so that the piston compressor valve can also be very quickly closed by the closure member without friction or with little friction.

The closing element is arranged in the reciprocating compressor valve in a smoothly movable manner in the direction of the extent of the axis of rotation, so that the closing element is automatically moved or displaced in the direction of the extent of the axis of rotation by the pressure difference existing across the reciprocating compressor valve between the inlet region and the outlet region or the pressure difference existing across the closing element.

The piston compressor valve advantageously comprises a first semi-rotating shaft (or first axle shaft), a second semi-rotating shaft (or second axle shaft) and a coupling which is arranged between the first and second semi-rotating shafts in such a way that the first and second plate rotating shafts can move or be displaced relative to each other in the direction of extension of the axes of rotation due to the coupling. The adjustment drive mechanism is preferably connected to the first semi-rotational axis and the closure member is fixedly connected to the second semi-rotational axis. The coupling is advantageously designed to be rotationally stable with respect to rotation about the axis of rotation, so that the closure element substantially or exactly follows the rotation of the adjustment drive when rotating about the axis of rotation. The coupling is designed to be smoothly movable in the direction of the extension of the axis of rotation, so that a pressure difference present across the closure automatically moves or displaces the closure in the direction of the extension of the axis of rotation. This ensures, on the one hand, a movement of the closing element in the direction of the extension of the axis of rotation and, on the other hand, a secure coupling of the closing element, preferably via a rotary shaft, to an adjustment drive, which drives the rotary shaft, which in turn causes a very rapid opening and closing of the closing element.

A plurality of variables are suitable as state variables for ascertaining the state of the piston compressor valve, in particular for ascertaining the position of the closure part relative to the valve seat, and there are thus, for example, movements, such as the closure part distance in the direction of the extent of the axis of rotation, preferably the distance between the closure part and the end face of the valve seat, or, for example, direct mutual contact between the closure part and the valve seat, or, in the case of a completely lifted closure part, the abutment of the closure part or the axis of rotation, or, for example, the pressure difference across the closure part of the piston compressor valve. A control device monitors the state variable, preferably compares it with a reference value, and opens and closes the closure element when a predetermined condition is met by correspondingly rotating the closure element or by actuating an actuating drive mechanism which rotates the rotational shaft. The piston compressor valve of the invention can thus be switched identically in a precise, rapid and repeatable way.

The device according to the invention or the method according to the invention has the following advantages: the lifting of the closure member off the valve seat can be determined in a very precise manner, on the one hand because the closure member can be automatically moved in the direction of the extension of the axis of rotation and, on the other hand, because it is particularly advantageous to measure the movement of the closure member or the distance between the closure member and the valve seat in the direction of the extension of the axis of rotation. The moment at which the closure member is lifted or lifted off the valve seat can thus be accurately grasped, and the adjustment drive can then be actuated immediately to rotate the closure member into the open position. Preferably, the closure member is rotated from the closed position to the open position by the adjustment drive mechanism after lifting off the valve seat for a period of at least 2 milliseconds up to 10 milliseconds. By opening quickly it is ensured that the fluid flowing through encounters a small flow resistance. Upon closing, the closure member is preferably rotated from the open position to the closed position by an adjustment drive mechanism for a period of at least 2 milliseconds up to 10 milliseconds, the closure member being automatically lowered towards the valve seat simultaneously or after completion of the rotation until the closure member abuts the valve seat.

In an advantageous design, the closing element is connected to the actuating drive via a torsion spring, wherein a portion of the kinetic energy is stored in the torsion spring, so that the closing element can be switched very quickly.

The valve closing element of a piston compressor valve comprising a valve seat and a closing element is preferably designed such that the valve seat has a center and a plurality of passage openings which are spaced apart in the circumferential direction and extend in the radial direction of the center, and the closing element has a plurality of radial arms and a rotational axis, wherein the arms extend in the radial direction of the rotational axis, and a closing part is assigned to each passage opening, wherein the width of the closing arm is designed such that the closing arm in the closed position completely covers the passage opening and in the open position covers the passage opening as little or not at all. The closing arms are designed such that the cross-sectional area of the closing arms decreases towards the outer periphery, thereby having a decreasing mass towards the outer periphery, since the closing arms are designed thinner towards the outer periphery, for example. A closure comprising such a closure arm has a particularly small mass towards the periphery and thus a reduced inertia, which is why a smaller force is required to operate, that is to say accelerate and brake, the closure in order to switch it back and forth between the closed position and the open position. The reduced inertia has the additional advantage that less force is required to accelerate the closure member in the direction of the extension of the axis of rotation, or the closure member can be moved more quickly or in a shorter time in the direction of the extension of the axis of rotation. The closure is particularly preferably made of plastic and preferably contains a fiber-reinforced material and preferably carbon fibers, so that the closure has a low mass.

Furthermore, a closure member comprising a plurality of radial arms has the advantage that the arms are not interconnected with each other at their outer periphery, so that each closure arm can place itself individually on the passage opening, so that each closure arm is better able to correct any irregularities or wear that may be present on the passage opening or on the closure arm, since each closure arm can be individually supported on the valve seat. The reduced cross-sectional area towards the outer periphery preferably results in a bending stiffness of the closure arm which also reduces towards the outer periphery, which brings the advantage that the closure arm can easily adapt to the contour of the valve seat when it covers the passage opening, which results in a particularly advantageous sealing.

In one advantageous design, the valve closing member for a piston compressor valve comprises a valve seat with a plurality of passage openings, a shaft with a rotational axis, a closure member rotatable about the rotational axis of the shaft for opening and closing the passage openings, wherein the closure member is fixedly connected to the shaft, the valve seat comprises a flat end side into which the passage openings open, wherein the valve seat has a center and the passage openings extend in a radial direction of the center, the closure member has a center point and a plurality of closure arms which extend in a radial direction of the center point, wherein the shaft is mounted in the valve seat in such a way that it is rotatable about the rotational axis and displaceable in the direction of extension of the rotational axis, wherein the rotational axis extends perpendicular to the end side and through the center, each closure arm having a sealing surface aligned towards the end side, and the closure arm is configured to be substantially complementary in shape to the passage opening to open and close the passage opening with the sealing surface in accordance with closure rotation.

The shaft is preferably designed to be displaceable in the longitudinal direction of the axis of rotation, so that the closure member can be automatically displaced in the longitudinal direction and in particular can be automatically lifted from the valve seat under the respective existing pressure difference.

The closing arm is preferably designed such that it has a cross-sectional area which decreases towards the periphery of the closing arm.

In an advantageous method for operating a valve closing member of a piston compressor valve, which valve closing member comprises a valve seat with a plurality of passage openings, a shaft with a rotational axis and a closure member fixedly connected to the shaft, wherein the shaft is mounted in the valve seat in such a way that the shaft is rotatable about the rotational axis and displaceable in the direction of the rotational axis, wherein the closure member for opening and closing the passage openings is rotated about the rotational axis, wherein the closure member is automatically lifted in the direction of the rotational axis due to the fluid pressure present on the piston compressor valve and is rotated after being lifted off the valve seat under active drive by the shaft, so that the passage openings are fully opened.

In an advantageous method, the closure element is lifted from the valve seat in a first method step in order to open the valve closing member, and after the lifting, the closure element is rotated into the open position in a second method step.

In an advantageous method, the position of the closure member relative to the valve seat is measured and the closure member is rotated about the axis of rotation only after the lifting off of the valve seat has been completed.

In an advantageous method, the closure member is rotated into the open position within a period of 2 milliseconds to 10 milliseconds after lifting off the valve seat.

Drawings

In the drawings for illustrating embodiments:

figure 1 shows a longitudinal section of a valve with a drive mechanism, when the closure member is against;

fig. 2 shows a longitudinal section through the valve according to fig. 1, with the closing member lifted;

FIG. 3 shows a perspective view of the valve seat;

FIG. 4 shows a perspective view of a closure member mated with the valve seat according to FIG. 3;

FIG. 5 shows a longitudinal section of the closure member and valve seat according to FIG. 6 along section line A-A;

FIG. 6 shows a perspective view of the closure member and valve seat with the closure member raised;

fig. 7 shows a perspective view of the device according to fig. 6, with the closure member in an open position;

fig. 8 shows a longitudinal section of the pressure valve, with the closing member lifted;

figure 9 shows a longitudinal section of another embodiment of the suction valve with the closing member raised;

fig. 10 shows a longitudinal section of the coupling;

fig. 11 shows a longitudinal section of another embodiment of the coupling;

FIG. 12 shows a longitudinal section of a bellows spring;

FIG. 13 shows a perspective view of another embodiment of a closure;

FIG. 14 shows a perspective view of another embodiment of a valve seat;

figure 15 shows a perspective view of the closure member in relation to the valve seat according to figure 14;

FIG. 16 shows a cross-sectional detail view along section line B of the valve of FIG. 14 in the closed state;

fig. 17 shows the view of fig. 16 when the closure is raised;

FIG. 18 shows the view of FIG. 16 with the closure lifted and rotated slightly;

FIG. 19 shows a perspective view of another embodiment of a valve seat;

FIG. 20 shows a partial perspective view of another embodiment of a closure;

FIG. 21 shows a side view of the radial closure portion of FIG. 20 from direction G-G;

FIG. 22 shows a cross-section of the closure portion of FIG. 21 along section line F-F;

FIG. 23 shows a cross-section of the closure portion of FIG. 21 along section line E-E;

FIG. 24 shows a side view from direction G-G of another embodiment of a radial closure;

FIG. 25 shows a cross-section of the closure portion of FIG. 24 along section line H-H;

FIG. 26 shows a cross-section of the closure portion of FIG. 24 along section line I-I;

fig. 27 shows a longitudinal section of another embodiment of the coupling;

fig. 28 shows a cross-section of the coupling of fig. 23 along section line C-C;

FIG. 29 shows a detail view of the electromagnetic drive mechanism;

FIG. 30 shows the electromagnetic drive mechanism of FIG. 29 with the armature in a second base position; and

fig. 31 shows another embodiment of the electromagnetic drive mechanism.

In principle, identical components are provided with the same reference numerals in the figures.

Detailed Description

Fig. 1 shows an actively controlled piston compressor valve 1, which comprises a valve seat 2 with a plurality of passage openings 2a, a closing element 3 which is rotatable about a rotational axis D for opening and closing the passage openings 2a, and an actuating drive 5 for rotating the closing element 3. The valve seat 2 has an end face 2b into which the passage opening 2a opens, wherein the closing part 3 is connected to the actuating drive 5 so as to be displaceable in the direction of extension L of the axis of rotation D, such that the closing part 3 can be rotated about the axis of rotation D and can be displaced relative to the end face 2b in the direction of extension L of the axis of rotation D. The shaft 4 is mounted in a bore 2e of the valve seat 2 or in an axially directed bearing. The valve 1 is arranged in a cage-shaped housing 6 which comprises a plurality of passage openings 6a and a cover 6 b. The closure member 3 is shown in a lowered closed position, whereby the closure member 3 abuts against the end side 2b of the valve seat 2 and the passage opening 2a is completely closed by the closure member 3. Furthermore, the valve 1 shown in fig. 1 comprises a sensor 8 for detecting a state variable E of the closure member 3 or the valve 1. The illustrated sensor 8 detects, for example, a movement of the shaft 4 in the extension direction L, for example a travel distance of the shaft 4. The control device 20 detects the values measured by the sensor 8 and also controls the actuating drive 5. By control of the control device 20, the closing member 3 is rotated in the direction of rotation of the axis of rotation D, preferably from the closed position to the open position or vice versa. In an advantageous embodiment, the control device 20 activates the actuator 5 as soon as the state variable E deviates from a predefined setpoint value. For example, the distance between the sealing surface 3d of the closure element 3 and the end face 2b of the valve seat 2, the distance of movement of the shaft 4 in the extension direction L, or the differential pressure Δ P, which is the difference between the pressure P2 on the one side of the closure element 3 and the pressure P1 on the other side of the closure element 3, are suitable as the state variable E. At least two sensors 8 are required to measure two pressures P1, P2. The shaft 4 is connected to a drive mechanism 5 in a manner not shown in detail, so that the shaft 4 is driven by the drive mechanism 5 on the one hand and the shaft 4 is displaceable in the longitudinal direction L relative to the drive mechanism 5 on the other hand with regard to rotation about the axis of rotation D. The closing part 3 is particularly advantageously automatically displaced in the direction of extension L, the pressure difference prevailing over the closing part 3 causing the closing part to be displaced in the direction of extension L, and the closing part 3 here either lifts off the valve seat 2 or approaches the valve seat 2 and finally abuts the end face 2b of the valve seat 2. In a preferred embodiment, the closure member 3 is mounted so smoothly that it can be displaced automatically in the extension direction L due to the pressure difference present. In another possible design, a drive mechanism (not shown) may also be provided, which at least partially causes the closing element 3 to move in the direction of extension L.

Fig. 2 shows the valve according to fig. 1, with the closing element 3 in a raised open position, in which the closing element 3 is raised in the longitudinal direction L relative to the end side 2 b. Furthermore, in the raised open position, the closure member 3 is preferably rotated about the axis of rotation D by means of the adjustment drive 5 relative to the closed position shown in fig. 1, such that the closure member 3 no longer covers the passage opening 2a, as shown in fig. 2 and 7, and the valve closing member 1a comprising the valve seat 2 and the closure member 3 is thus permeable to fluid in the longitudinal direction L. In contrast to the sensor 8 shown in fig. 1, the sensor 8 shown in fig. 2 measures the distance from the end side 4c of the shaft 4. The closure member 3 is fixedly connected to the axis of rotation D or the shaft 4 such that the closure member 3 immediately follows a rotation about the axis of rotation D and such that the axis of rotation D or the shaft 4 immediately follows a movement of the closure member 3 in the longitudinal direction L.

Fig. 3 shows a first exemplary embodiment of a valve seat 2 in a perspective view, which has a central bore 2e or center Z and a plurality of passage openings 2a, which extend in the radial direction of the central bore 2e and have a connecting edge 2f extending therebetween. The valve seat 2 also has an end face 2b into which all the passage openings 2a open, wherein in an advantageous embodiment the end face 2b also has an annular bearing surface 2 c. The illustrated valve seat 2 has twenty-five passage openings 2a which are distributed uniformly or at equal distances from one another in the circumferential direction, wherein in one embodiment each passage opening 2a has a circumferential angle of 7 ° and each connecting edge 2f has a circumferential angle of 7.4 °. In order to rotate the closure from the open position into the closed position or the closed position, respectively, or vice versa, the closure must therefore be rotated through a rotation angle of 7.2 °. The valve seat 2 advantageously comprises at least twenty passage openings 2a, which are circumferentially spaced apart, and a corresponding equal number of closing arms 3a, opposite to which the closing arms 3a are circumferentially spaced apart to open and close the passage openings 2 a. The design with at least twenty passage openings 2a and radial arms 3a has the advantage that the maximum rotation angle required for the closure is relatively small and in this embodiment is 360 deg. divided by 20 (the number of passage openings) divided by 2 (half the angle has to be rotated), thus 9 deg..

Fig. 4 shows a perspective view of the closure member 3 mated with the valve seat 2 according to fig. 3. The closure 3 comprises a hub 3e with a central hole 3c and comprises a plurality of closure arms 3a extending in radial direction of the central hole 3c or rotation axis D and spaced apart by a gap 3b and extending to an outer periphery 3 s. In one embodiment, each recess 3b has a circumferential angle of 7 ° and each closing arm 3a has a circumferential angle of 7.4 °, so that the closing arm 3a is designed to be slightly wider than the passage opening 2a, so that the passage opening 2a can be completely covered by the closing arm 3a in the respective adjustment situation of the closure member 3. The closure part 3 is preferably designed in one piece or unitary (that is to say consists of one part), advantageously made of plastic, for example of fiber-reinforced plastic, in particular carbon fiber-reinforced plastic (CFP). CFP is a composite material in which carbon fibers are embedded in a plastic matrix material, most often an epoxy resin. The matrix material is used to connect the fibers and fill the voids. Other durable plastics or thermosets are also suitable as matrix materials. But the closure can also be made of plastic without added fibres.

Fig. 6 and 7 show a practical valve closing member 1a comprising a closing member 3 and a valve seat 2 in two possible relative positions. Furthermore, fig. 5 shows the closure member 3 shown in fig. 6 and a section through the valve seat 2 along section line a-a. The valve closing member 1a, i.e. the closing member 3 and the valve seat 2, can have basically four different relative positions, in particular a lowered closing position, a raised opening position and a lowered opening position. Lifting means that the closure member 3 is lifted relative to the valve seat 2 and is thus spaced from the valve seat 2, as shown in fig. 2 and 5-7. Lowering means that the closure member 3 abuts the valve seat 2 as shown in figure 1. The valve 1 or the valve closing member 1a is only completely closed in the lowered closing position shown in fig. 1, the closing member 3 abutting against the valve seat 2 and the passage opening 2a being completely closed by the closing member 3 or the closing arm 3a of the closing member 3 abutting thereon. In the raised closed position shown in fig. 5 and 6, the closure member 3 is spaced from the valve seat 2, wherein the closure member 3 or its closure arms 3a respectively cover the passage opening 2a in a spaced manner, so that only a small gap S exists between the closure member 3 and the valve seat 2, into or out of which fluid can flow. In the raised open position shown in fig. 7, the closure member 3 is spaced from the valve seat 2, wherein the closure member 3 is rotated in the direction of rotation D1 relative to the position of fig. 6, such that the passage opening 2a is no longer covered by the closure member 3 or its closure arm 3a in the longitudinal direction L or in the direction of extension along the axis of rotation D, or at most overlaps at the edges to a minimum extent, so that the largest possible area of the passage opening 2a is open in the longitudinal direction L towards the circulating fluid, the fluid flowing through the fully open valve closure part 1a being unimpeded or only negligibly impeded by the closure member 3 or its radially extending closure arm 3 a. If the closure member 3 shown in fig. 7 is to be lowered so that said closure member 3 abuts against the valve seat 2, the closure member 3 will be in a lowered, open position in which the passage opening 2a is maximally, preferably fully, but at least maximally open, wherein the maximum opening area is determined by the circumferential width of the respective closure arm 3a and the circumferential width of the respective passage opening 2 a. The closure 3 is opened and thus moved to the open position by rotation of the adjustment drive mechanism 5 in the rotational direction D1, and is closed and thus moved to the closed position by rotation in the rotational direction D2. Furthermore, by means of a force acting on the closing part 3, in particular a fluid pressure difference, the closing part 3 is automatically moved in the longitudinal direction L, so that the closing part 3 is raised or lowered in this direction relative to the valve seat 2. As shown in fig. 6, the axis of rotation D extends through the centre point M of the closure member 3 or the centre Z of the valve seat 2. Fig. 7 furthermore shows that the closing element 3 has a fastening side 3g, on which fastening holes 3h are provided for fastening the closing element 3 to the shaft 4.

Fig. 5 shows a cross section along the sectional line a-a of fig. 6. The closure member 3 is lifted relative to the valve seat 2. The closure 3 comprises a hub 3e having a centre point M, which hub 3e comprises a central hole 3c, a flat sliding surface 3f and a fixation side 3 g. The closing arm 3a is tapered radially outward, so that its cross-sectional area decreases toward the outer periphery 3 s. The advantage of tapering is that the mass of the closing arm 3a decreases towards the outside, which reduces the weight and inertia of the closure member 3. In the embodiment according to fig. 5, the height 3t of the closing arm 3a decreases towards the outer periphery 3 s. The closing arm 3a has a constant height 3t in the circumferential direction D; in this case, the closing arm 3a has a constant height 3 t. This means that the closing arm 3a has the same height 3t over its entire width.

In one exemplary method, the piston compressor valve 1 shown in fig. 1 and 2 can be operated such that a state variable E of the closing member 3, for example a displacement distance S1 of the shaft 4 in the longitudinal direction L, is measured, wherein the closing member 3 is initially arranged in a lowered closed position as shown in fig. 1, wherein the shaft 4 can be automatically moved in the longitudinal direction L and the closing member 3 can be lifted from the valve seat 2 depending on the working gas pressure acting on the valve 1 or the closing member 3. As soon as the state variable E exceeds a predetermined target value, the state variable E is detected and the drive 5 is activated, so that the closing part 3 is pivoted by the drive 5 about the axis of rotation D into the raised open position shown in fig. 2, wherein the rotation is produced by the drive 5 and the lifting in the longitudinal direction L is carried out automatically. The displacement signal of the sensor 8 is used as the state variable E by measuring the displacement of the shaft 4 in the direction of the longitudinal axis L, wherein the displacement preferably corresponds to the distance between the closing element 3 and the end side 2 b. As soon as the state variable E exceeds a predetermined setpoint value, for example 0.1mm, the drive mechanism 5 is activated and the closure element 3 is rotated into the open position shown in fig. 2 or 7.

Fig. 8 shows a valve 1 designed as a pressure valve, in which the closing member 3 is in a raised closed position. The closure member 3 is arranged between the valve seat 2 and the drive mechanism 5. In contrast, in fig. 2, the valve seat 2 is arranged between the closing element 3 and the drive mechanism 5. The valve according to fig. 8 comprises a first shaft part 4a or first semi-rotational shaft and a second shaft part 4b or second semi-rotational shaft connected to each other by a coupling 9. The first shaft portion 4a is not movable in the longitudinal direction L, while the coupling 9 allows movement in the longitudinal direction L, so that the second shaft portion 4b is movable in the longitudinal direction L. In the exemplary embodiment according to fig. 8, the bore 2e or the axial guide bearing is designed as a blind bore in which the second shaft part 4b is guided in the radial and axial direction. In other respects, the components, namely the valve seat 2, the closure member 3, the drive mechanism 5 and the cage housing 6, have already been described in the context of fig. 1 and 2. In another embodiment, the second shaft portion 4b can be omitted and the closure member 3 is directly connected to the coupling 9. The coupling 9 is preferably designed to be elastic or springy in the longitudinal direction L, so that the closing member 3 can move automatically in the longitudinal direction L due to the flow forces acting.

Fig. 9 shows another valve 1 in the form of a suction valve. In contrast to the valve 1 according to fig. 2, the valve 1 according to fig. 9 has a torsion spring 7 which comprises an inner torsion spring 7a and an outer hollow torsion bar 7 b. One end of the internal torsion spring 7a is connected to the drive mechanism 5, and the other end is connected to the hollow torsion bar end 7d of the external hollow torsion bar 7 b. One end of the hollow torsion bar 7b is connected to the cover 6b by a fastener 7c, and the other end is connected to the hollow torsion bar end 7 d. The hollow torsion bar end 7d is connected to a hollow cylindrical connection portion 10 in which the sensor 8 is arranged. The connecting portion 10 is connected to the shaft 4 by a coupling 9. The coupling 9 is designed such that it can change its length in the longitudinal direction L. The coupling is preferably designed to be resilient, preferably spring-resilient, in the longitudinal direction L. Thus, the shaft 4 is arranged to be movable or displaceable in the longitudinal direction L with respect to the connecting portion 10 or the torsion spring 7 by means of the coupling 9. The torsion spring 7 is designed to be immovable in the longitudinal direction L. The drive mechanism 5 causes the inner torsion spring 7a to rotate and also rotates the outer hollow torsion bar 7b via the hollow torsion bar end 7 d. Furthermore, by rotating the hollow torsion bar end 7d, the connecting portion 10 and the coupling 9 and thus the shaft 4 are rotated. The coupling 9 is configured such that the coupling 9 allows a length variation in the longitudinal direction L and preferably has a spring action, in particular an elastic property. The coupling 9 preferably has the desired rigidity characteristics with respect to rotation about the rotation axis D, so that the closure member 3 and the shaft 4 are non-rotatably connected to the connecting portion 10 and the hollow torsion bar end 7D by the coupling 9. Publication WO2009/050215a2 discloses in detail one possible valve operation method. The content of said publication is hereby incorporated into the present patent application.

Fig. 10 shows a longitudinal section through a further embodiment of the connection between the torsion spring 7 and the shaft 4, wherein the connection is formed by a coupling 9 which is movable in the longitudinal direction L and has in particular a spring elasticity. The coupling 9 is preferably designed to be as rigid as possible, preferably rotationally stable, with respect to rotation about the axis of rotation D. The coupling 9 shown in fig. 10 is designed as a bellows spring. The bellows spring 9 is preferably made of metal in order to achieve a high torsional stiffness when rotating about the axis of rotation D. The bellows spring 9 is designed such that the bellows spring 9 is elastic in the longitudinal direction L, wherein the elastic properties can be determined, for example, by the wall thickness of the bellows spring, the material chosen (preferably metal) and the geometry of the bellows spring. In one advantageous embodiment, a sensor 8 is arranged in the interior 9g, which sensor measures a distance in the longitudinal direction L, for example a distance from the end side 9f of the bellows spring 9 arranged opposite thereto. In a particularly advantageous embodiment, the coupling 9 forms an interior 9g which is sealed off from the outside in a gas-tight manner, so that contaminants originating from the outside do not settle in the interior 9g, as a result of which the sensor 8 can measure the distance to the end side 9f in a long-term reliable and maintenance-free manner. The coupling 9 shown in fig. 11 can also be used, for example, in a valve 1 as shown in fig. 1, 2 or 8, by the fact that the continuous shaft 4 is divided into a first shaft part 4a and a second shaft part 4b, and that the two shaft parts 4a, 4b are connected to the coupling 9, as shown in fig. 10, so that the shaft 4 shown in fig. 1, 2 or 8 has a springing characteristic in the longitudinal direction L by means of the coupling 9 arranged on the shaft 4.

Fig. 11 shows a longitudinal section of another embodiment of the connection between the torsion spring 7 and the shaft 4, wherein the connection comprises a combination of a hollow cylindrical connection part 10 and a coupling 9, wherein the coupling 9 is designed as a bellows spring, as shown in fig. 10 or 12. In an advantageous embodiment, a sensor 8 is arranged in the connecting section 10, which sensor measures, for example, the distance to the end side 9f of the bellows spring 9 opposite thereto. In a particularly advantageous embodiment, the connection part 10 and the coupling 9, which is also designed as a bellows spring 9, form a common interior 9g which is sealed off in a gas-tight manner from the outside. The arrangement shown in fig. 11 comprising the connection part 10 and the bellows spring 9 can also be used in a valve 1 as shown in fig. 1, 2 or 8, for example. For example, an eddy current sensor is suitable as the sensor 8.

Fig. 12 shows a further embodiment of a coupling 9 comprising a bellows-like, preferably metallic, outer shell 9i with bellows-like protrusions 9k and an inner space 9g, which is partly filled with an elastic filling material (shown in hatched lines), for example, so as to leave an open cylindrical inner cavity 9h again. The elastic filling material serves to determine the spring rate or the spring elasticity of the coupling 9 in the longitudinal direction L, wherein the spring rate is determined in particular by the elasticity of the filling material and/or the arrangement of the filling material in the bellows-like projections 9k of the housing 9 i. The resilient filler material is preferably composed of a resilient plastic material. An elastic filler material is provided in the lumen 9h, wherein at least some of the bellows-like protrusions 9k (preferably all protrusions 9k as shown) are preferably completely filled with the elastic filler material 9 g. For a reliable automatic movement of the closing element 3 in the longitudinal direction L, the coupling requires a spring rate which is adapted to the forces acting on the closing element 3 in the longitudinal direction L. The coupling 9 shown in fig. 10-12 can be manufactured with a variety of different spring rates as desired.

Fig. 13 shows a perspective top view of a further embodiment of the closing element 3. The underside of the closure 3 can be designed as shown in fig. 4. The closure 3 comprises a hub 3e having a central hole 3c, a centre point M and a plurality of closures 3a extending in radial direction of the centre point M and spaced from each other in circumferential direction. Each radial arm 3a is composed of a plate-like portion 3w and a rib 3i fixedly connected thereto, wherein each plate-like portion 3w extends radially to the outer periphery 3 s. The side of each rib 3i facing away from the passage opening 2a projects beyond the plate-like portion 3w in the direction of the rotation axis D. The height 3t of the rib 3i decreases toward the outer periphery 3s, and thus has a decreasing cross-sectional area. The bending stiffness of the closed portion 3a depends inter alia on the design of the projecting ribs 3 i. The height 3t of the ribs 3i advantageously decreases radially towards the outside, so that the mass of the ribs 3i decreases towards the outside, and in particular radially outwards, so as to thereby reduce the inertia of the closure member 3, in particular in connection with a rotational movement about the axis of rotation D.

Fig. 14 shows a perspective top view of the valve seat 2, which, in contrast to the exemplary embodiment shown in fig. 3, has support elements 2D which project in the direction of the axis of rotation D on the annular surface 2c and are spaced apart from one another in the circumferential direction, preferably in an ordered manner, and the support elements 2D extend radially relative to the bores 2 e. Fig. 15 shows a perspective view of a closure element 3 which, in contrast to the embodiment shown in fig. 4, has recesses 3k on the surface of the hub 3e, which extend radially with respect to the central bore 3c and are arranged opposite one another to the support element 2 d. The valve seat 2 according to fig. 14 and the closure member 3 according to fig. 15 are designed to be adapted to one another in such a way that the same number of projecting support elements 2d and recesses 3k are arranged in such a way that one opposing recess 3k is provided for each support element 2d and in which opposing recess 3k the respective support element 2d can engage. Fig. 16-18 show the valve seat 2 and the closure member 3 in different positions in a sectional view along section line B of fig. 14. In fig. 16, the closure member 3 has a lowered closed position, in which the closure member 3 abuts against the valve seat 2 and each support element 2d engages in a recess 3k arranged opposite thereto, wherein the protruding support element 2d is completely accommodated in the recess 3k, so that the bearing surface 2c lies flat against the hub 3 e. In the case of fig. 17, there is an upward positive pressure difference Δ P on the closure member 3, which results in the closure member 3 being lifted in the longitudinal direction L relative to fig. 16, so that the closure member 3 is in a lifted closed position in which the closure member 3 is lifted, but has not yet been rotated about the axis of rotation D relative to the position according to fig. 16. Once the closure member 3 is in the position shown in fig. 17, the closure member 3 is rotatable about the axis of rotation D. Fig. 18 shows the closure element 3 in a raised position, in which the closure element 3 is raised in the longitudinal direction L relative to fig. 16 and the closure element 3 is rotated in the direction of rotation of the axis of rotation D. Fig. 18 shows the situation that a negative pressure difference Δ P is present downwards on the closure member 3, which results in the closure member 3 wanting to be lowered towards the valve seat 2, but this is prevented by the support element 2d against the closure member 3. The end surface of the support element 2D abutting against the closing member 3 is relatively small, which brings about the advantage that the rotational force required to rotate the closing member 3 in the rotational direction D2 of the rotational axis D is relatively small. The support element 2d thus has the advantage that the resistance to rotation between the closure member 3 and the valve seat 2 is reduced compared to an embodiment without the support element 2d, so that the closure member 3 can be reliably rotated even if a negative pressure difference Δ P exists across the closure member 3 as shown, which pressure difference Δ P pushes the closure member 3 towards the valve seat 2. Thus, the valve 1 of the present invention can operate reliably over a wide range of stored pressure differentials. Another advantage of the support element 2d in the case of a negative pressure difference Δ P is the reduction of wear on the closure member 3 and the valve seat 2, given that the closure member 3 and the valve seat 2 rotate relative to each other in the case of a negative pressure difference Δ P.

In another embodiment, instead of the support elements 2d, recesses may be provided on the valve seat 2, and instead of the recesses 3k, support elements may be provided opposite each other in the closure member 3.

Fig. 19 shows a further exemplary embodiment of a valve seat 2 which, in contrast to the exemplary embodiment shown in fig. 3, has a plurality of rolling elements 12 which are spaced apart in the circumferential direction in the annular surface 2 c. The rolling elements 12 project slightly beyond the annular surface 2c, for example by 1/10 mm. The rolling elements 12 serve to reduce the sliding or rolling resistance of the rotating closure member 3 which bears on the valve seat 2 or the annular bearing surface 2 c. The rolling elements 12 are preferably of cylindrical or conical design and are preferably made of metal or ceramic.

Fig. 20 shows a detail of another embodiment of a closure 3 comprising a hub 3e with a central hole 3c and comprising a plurality of radial closures 3a arranged circumferentially spaced from each other and connected to the hub 3 e. Fig. 21 shows a side view of a single closing part 3a according to fig. 20, seen from the direction G. Fig. 22 shows a longitudinal section F-F of the closing part 3a and fig. 23 shows a cross section of the closing part 3a along a sectional line E-E. The closing portion 3a comprises first and second radial side walls 3m, 3n and a cover surface 3r, which define an inner space 3 o. The first and second radial side walls 3m, 3n extend in this manner, and the side walls 3m, 3n also form a flat sealing surface 3d, respectively, which is aligned toward the valve seat 2, as shown in fig. 23. The two sealing surfaces 3d can, as shown in fig. 22, together with the sealing surface 3d arranged on the hub 3e and the sealing surface 3d arranged in the region of the outer periphery 3s of the closure part 3a rest against the end side 2b of the valve seat 2 and seal the passage opening 2a, for example in the case of the valve seat 2 according to fig. 3, the sealing surface 3d rests against the end side 2 b. The closing element 3 in the lowered, closed position bears on the valve seat 2, wherein the closing element 3 is arranged relative to the valve seat 2 in such a way that the sealing surface 3d abuts against the end side 2b and closes the passage opening 2a, wherein the scoop-shaped inner space 3o of the closing part 3a is now higher than and in fluid communication with the passage opening 2 a. The advantage of the closure element 3 shown in fig. 20 to 23 is that the radial closure part 3a has a high rigidity, in particular with the aid of the side walls 3m, 3n, with a corresponding choice of material, while on the other hand the radial closure part 3a can be designed to be lightweight, which brings about the advantage that the closure element has a reduced inertia when the closure element 3 is rotated about the axis of rotation D. Therefore, in order to rotate the closing member 3 about the rotation axis D, in particular in the acceleration phase and the braking phase, less force is required to move the closing member 3 from the open position to the closed position or vice versa.

Fig. 24 shows a side view of another embodiment of a single closing part 3a, again seen from direction G. Fig. 25 shows a longitudinal section of the closure part 3a according to fig. 24 along a sectional line H-H, and fig. 26 shows a cross section of the closure part 3a along a sectional line I-I. The closing part 3a further comprises a first and a second radial side wall 3m, 3n and a cover surface 3r, wherein the radial side walls 3m, 3n are designed to be wider and to protrude beyond the cover surface 3r as shown in fig. 24-26 compared to the embodiment according to fig. 21-23. The side walls 3m, 3n, which are wider in the direction of extension of the axis of rotation D, have the following advantages: with the same wall thickness of the side walls 3m, 3n, the radial closure 3a has a high stability or a high bending stiffness, or the side walls 3m, 3n are designed to be thinner, so that the closure 3a has a lower mass. All the closure parts 3a of one closure 3 are advantageously designed in the same way.

Fig. 27 shows a longitudinal section of a further embodiment of the coupling 9, which is an alternative to the coupling 9 according to fig. 10 and 11. Fig. 28 shows a section of the coupling according to fig. 27 along the sectional line C-C. As already described in fig. 10 and 11, the coupling 9 shown in fig. 27 and 28 is also displaceable in the longitudinal direction L, while the coupling 9 is torsionally stiff with respect to rotation about the axis of rotation D. The coupling 9 comprises a first coupling part 9a fixedly connected to the first shaft part 4a and a second coupling part 9b fixedly connected to the second shaft part 4 b. The first coupling part 9a comprises an angular groove 9D and the second coupling part 9b comprises an angular protrusion 9c, wherein the groove 9D and the protrusion 9c are designed to match each other such that a relative movement in the longitudinal direction L is possible, wherein a relative rotation about the rotation axis D is hardly or not possible at all. The first and second coupling parts 9a, 9b are connected to each other in a spring-elastic manner by means of an elastic spring part 9e, so that the first and second coupling parts 9a, 9b can be moved relatively in the longitudinal direction L. As shown, the spring part 9e can be designed as a hollow cylinder and made of plastic, for example. In an advantageous design, the sensor 8 is arranged in the coupling 9 as shown, which measures the distance or the change in distance between the two coupling parts 9a, 9b, for example by measuring the distance between the sensor 8 and the end side 9 f. In one advantageous embodiment, the coupling 9 has a stop 9l, which defines the maximum travel distance of the coupling 9. The elasticity of the spring portion 9e is preferably selected such that the closing member 3 is automatically movable in the longitudinal direction L.

Fig. 29 shows the electromagnetic drive 5 in the first basic position, and fig. 30 shows the same electromagnetic drive 5 in the second basic position. The drive mechanism 5 includes a stator 5a having four yokes 5b and an inner space 5c for coils. Not shown are conductive coils for generating a magnetic field wound around each of the four yokes 5b and extending in the inner space 5 c. Furthermore, the drive mechanism 5 comprises an armature 5D, which is preferably fixedly connected to the shaft 4 or the torsion spring 7 and is mounted pivotably about the axis of rotation D. The drive mechanism 5 is designed such that the maximum pivoting range of the armature 5d is slightly greater than the angle required to rotate the closing member 3. Depending on the design, the drive mechanism 5 preferably has a pivot angle in the range from 5 ° to 20 °. Rotating the closure member 3 from the open position to the closed position of 7.2 ° means that the open position and the closed position together circumferentially occupy a total of 14.4 ° of rotation, so that the valve seat 2 has twenty-five passage openings 2a which are uniformly spaced from one another in the circumferential direction, as shown in fig. 3. The armature 5d of the drive 5 will therefore have to be rotated through a slightly larger angle, for example through an angle in the range from 8 ° to 10 °, depending in particular on the torsional rigidity of the first shaft part 4 a. The valve seat 2 shown in fig. 3 has the following advantages: a small angle of rotation is required from the open position to the closed position, so that a particularly rapid switching or a particularly short switching time can be achieved. The drive mechanism 5 shown in fig. 29-31 is adapted to rotate the closing member 5 as shown in fig. 1, 2, 8 and 9 through an angular range of, for example, 7.2 deg. in order to drive the closing member 5 and rotate the latter from the open position to the closed position or vice versa.

In a particularly advantageous embodiment, as shown in fig. 31, a damping element 5f is provided at the end of the armature 5d, which damping element has the task of preventing the armature 5d from coming into direct contact with the yoke 5 b. The damping element 5f is made of a non-magnetic material, such as aluminum or a plastic material. The advantage of this design is that the armature 5d is prevented from sticking to the yoke 5b, thereby ensuring that the armature 5b immediately disengages from the yoke 5b when a corresponding magnetic field for switching the armature 5d is applied to the drive mechanism 5. The piston compressor valve 1 as shown in fig. 1, 2, 8, 9, comprising the drive mechanism 5 as shown in fig. 29-31, can be switched very quickly from a closed position to an open position and vice versa, wherein the switching time is less than 0.1 seconds, particularly advantageously in the range of about 2.5 milliseconds, or in the range of 2 to 10 milliseconds.

It is not necessary to measure the angle of rotation of the closing member 3 as the state variable E of the closing member 3, since no indication can be derived from said state variable as to the displacement of the closing member 3 in the longitudinal direction L, and therefore the moment at which the adjustment drive 5 will be activated cannot be determined on the basis of said state variable. However, for reliable operation of the piston compressor valve, it may prove advantageous if the angle of rotation of the closing part 3 or a variable associated therewith, in particular the angle of rotation of the actuating drive 5, can also be additionally measured. It is also advantageous to measure the crankshaft angle of the compressor. By means of the compressor crank angle it is possible to determine when or at which crank angle the piston compressor valve has to be opened or closed, or at which crank angle the discharge or intake of the piston compressor valve takes place. A malfunction of the closing member 3 can be detected, for example, by measuring the angle of rotation of the closing member 3 and a malfunction signal can be generated, or the reciprocating compressor can be stopped in an emergency, for example, if the closing member 3 is not opened and closed by rotation of the closing member 3 in a period predetermined by the crank angle.